Infinitely variable speed transmission



April 20, 1943. w. H. JOHNSON I INFINITELY VARIABLE SPEED TRANSMISSION 15 Sheets-Sheet 1 4 N3 m m 5 i 7 \MW 3 4 93 0 g 0930 3 h g V g g g m Q @fi Nu HIIIIHIIIAL 2 d] A? ML April 20, 1943. w. H. JOHNSON 2,316,

' INFINITELY VAR'IABLESREED TRANSMISSION Filed Jan. 22, I940 15SheetS-Sheet 2 1 1 zea- INVENTOR April 20, 1943. w. H. JOHN-SON 2,316,793

INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Slieet s ATTORNE April 20, 1943. w. H. JOHNSON 2,316,79

INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Shets-Sheet 4 INVENTOR ATTORNEY April 20, 1943. w. H. JOHNSON 2,316,793

INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet 5 ATTORNEY April ,1943. w. H. JOHNSON 2,316,793

INFINITELY VARIABLE SPEED TRANSMISSION Fil ed JanQ 22, 1940 15 Sheets-Sheet s INVENTOR f F 7 A RNEY April 1943- w. H. JOHNSON I 2,316,793

INFINITELY VARIABLE SPEED TRANSMISSION F'iled' Jan. 22, 1940 15 Sheets-Sheet '7 INVENTOR ATTORNE April 20., 1943. w. H. JOHNSON INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet 8 .2 y a Z ATTO NEY April 26, 1943. w. H. JOHNSON 2,316,793

INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan 22, 1940 15 Sheets-Sheet 9 4 1) INYENTOR BY 2. ATTORNEY April 20, 1943. w. H. JOHNSON 2,316,793

' INFINITEL-Y VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet l0 ATTORNEY April 20, 1943. ,w. H. JOHNSON INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet 11 I INVENTOR Q ATTORN EY w. H. JOHNSON INFINITELY VARIABLE SPEED TRANSMISSION April 20, 194-3.

Filed Jan. 22, 1940 15 Sheets-Sheet 12 ill/law I W INVENTOR 1 $1M W I ATTORNEY April 20, 1943. w. H. JOHNSON INFINITELY VARIABLE SiEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet 13 a) 161,. W) ATTORNEY April 20, 1943. w. H. JOHNSON INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-Sheet 14 w INVENTOR m M%MM, v 71 ATTO EY April 20, 1943. w. H. JOHNSON 2,316,

INFINITELY VARIABLE SPEED TRANSMISSION Filed Jan. 22, 1940 15 Sheets-$11961. 15

FULCEUM DRJVEN DRIVE.

INVENTOR 1/. ATTORNEY Patented Apr. 20, 1943 I INFINITELY VARIABLE SPEED TRANSMISSION William Horace Johnson, 'Cranston, R. I., assignor to Weskenson Corporation, Providence, R. 1., a corporation of Rhode Island Application January 22, 1940, Serial No. 314,930

31 Claims.

The invention relates to transmission and more particularly to transmissions having infinitely variable speed ratios.

According to a preferred form, the transmission comprises a, driving member in the form of a cam, or a discontinuous or segment gear, or both, driving reciprocating slide or rack members. Each rack member is connected to a working beam having a fulcrum point whose position is adjustable to Vary the speed ratio. The working beams drive reciprocating driven racks which drive respective overrunning clutches on the driven shaft. If desired, a master clutch may be interposed between the driving shaft and the driving cams or discontinuous gear and a second master clutch may be interposed between driving and driven shafts, these clutches acting in conjunction. The second master clutch may be engaged for direct drive, after which the first clutch may be disengaged to throw out the reciprocating slides and working beams from operation. If desired, a special torque limiting device may be incorporated in the driven shaft to protect the transmission and related parts from the high torques which may be developed when the transmission is adjusted to provide high ratios.

The invention also consists in certain new and original features of construction and combination of parts hereinafter set forth and claimed.

Although the novel features which are believed to be characteristic of this invention will be particularly pointed out in the claims appended hereto, the invention itself, as to its objects'and advantages, and the manner in which it may be carried out, may be better understood by referring to the following descripton taken in connection with the accompanyin drawings forming a part thereof, in which Fig. l is an outside-side elevation of the transmission complete;

Fig. 2 is an outside front end elevation of the transmission complete;

Fig. 3 is an outside rear end .elevation of the transmission complete;

Fig. 4 is a plan view taken on the line 4-4 of Fi 1; 3

Fig. 5 is a plan section taken on the line 5-8 of Fig. 1;

Fig. 6 is a vertical longitudinal on the line 86 of Fig. 2; Y

Fig. 7- is a vertical section taken on the line section taken Fig. 8 is a vertical section taken on the line 0-8 of Fig. 6 with lower slide shown at end of its stroke;

Fig. 9 is a vertical section taken on the line -99 of Fig. 6;

Fig. 10 is a vertical section taken on the line Ill-III ofFig. 6;

Fig. 11 is a vertical section taken on the line ll--ll of Fig. 6;

Fig. 12 is a vertical section taken on the line l2-I2 of Fig. 6;

Fig. 13 is a vertical section taken on the lines I3l3 of Figs. 5 and 16; Fig. 14 is a vertical section taken on the lines 14-44 of Figs. 5 and 16;

Fig. 15 is a vertical section taken on the line l5-l5ofFig. 6; Fig. 16 is a vertical section taken on the line l6-i 6 of Fig. 6;

Fig. 17 is a vertical section taken on the line I'|--l1 of Fig. 16;

Fig. 18 'is a view of one of the control sliding key assemblies shown in Figs. 13 and 16;

Fig. 19 is a view of the other control sliding key assemblies shown in Figs. 1'3 and 16;

' on the line 20-20 of Fig. 6;

Fig. 21 is a detail illustrating the collar for operating the control key for the overrunnin clutches;

Fig. 22 is a longitudinal section through the driven shaft taken on the line 22-22 of Fig. 5;

Fig. 23 is a section taken on the line 23-23 of Fig. 22;

Fig. 24 is a section taken on the line 24-24 of Fig. 23

Fig. 25 is a section taken on the line 2525 of Fig. 23;

Fig. 26 is a fragmentary diagrammatic view illustrating the relation between the segment gear and the racks and illustrating the transfer of the power drive from one rack to the other;

Fig. 27 is a vertical section illustrating the relation'between the control cams and followers and between the segment gear and power racks;

Fig. 28 is a section on the line 28-28 of Fig. 27;

Fig. 29 is a diagrammatic view illustrating the general layout of the transmission;

Figs. 30, 31 and 32 are diagrammatic views illustrating the operation of the working beams for changin the speed ratio from, forward through neutral to reverse.

, In the following description and in the claims,

' various details will be identified by specific names for convenience, but they are intended to be as generic in their application as theartwm per-' mit,

Like reference characters denote like parts in the several figures of the drawings.

In the drawings accompanying and forming part of this specification, certain specific disclosure of the invention is made for purposes of explanation, but it will be understood that the details may be modified in various respects without departure from the broad aspect of the invention.

Referring now to Figs. 1, 2 and 3, the transmission consists, in general, of a two-part case, a lower part 2|, an upper part 22'and cover 23, a driving shaft 24 adapted to be connected to an automobile or other prime mover and a driven shaft 25 adapted to be connected to a propeller shaft of an automobile or other load shaft. Cover 23 has a filling device for lubrication at 26I. Case 2| has draining means at 252. Case 2| has mounting supports at 263, 264, 265 and 266. Cases 2| and 22 are bolted together by a series of screws 261. Cover 23 is bolted to upper case 22 by a series of screws 268.

The invention will first be briefly described with reference to Fig. 29. Located between the driving shaft 24 and driven shaft 25 within the case are the operating parts shown diagrammatically in Fig. 29. The drive shaft 24 is connected through a suitable main clutch 21 to an intermittent gear 32 meshable with a pair of racks 34' and 35 mounted on reciprocating slides 49 and 4|. Suitable cams are provided operating on suitable followers for controlling the movement of said slides 49 and 4| to cause the racks 34 and 35 alternately to engage said intermittent gear. These slides 49 and 4| are connected to working beams 82 and H2 which are fulcrumed 'on suitable fulcrum slides 85 and H5, slidable to vary the speed ratio. The driven ends of the working beams are pivoted to driven slides carrying rack members I94 and I34, driving pinions I95 and I35 which are connected through overrunning clutches III! and I38 to the driven shaft 25. A disconnect clutch 28 directly connects drive shaft 24 with driven shaft 25. A suitable torque limiting device 239 may be incorporated in driven shaft 25 to prevent breakage of connected parts under the very high torques obtainable with very high ratios.

Main clutches 21 and 28 may be interconnected so that one is engaged while the other is disengaged, and vice versa, with provision for overlap to prevent break in power flow. For direct drive clutch 28 is engaged and clutch 21 is disengaged, thus providing a direct drive from shaft 24 through to shaft 25 without-driving any of the reciprocating or oscillating parts. To obtain speed change, clutch 21 is engaged and clutch 28 is disengaged, thus driving the intermittent gear 32, reciprocating the slides 49 and 4| back and forth. This in turn reciprocate-s the working beams 82 and 2 about their fulcrum points. which in turn reciprocate the driven racks I94 and I34, which in turn drive gears I95 and I35, which in turn drive thedriven shaft 25 through the overrunning clutches I I9 and I38.

The construction and operation of these parts are explained more in detail hereinafter.

Referring now to Fig. 13, the parts more or less directly associated with drive shaft 24 will now be described. n outer end of driving shaft 24, on splined portion I83, is mounted an adapter I to which, in the case of a motor vehicle drive. a flywheel can be bolted. This adapter is secured by nut I16. On the hub of adapter I15 is mounted an oil seal I11 and an anti-friction bearing I18 secured in place by nut I19. Bearing I18 is mounted in bore I89 at the junction of cases 2| and 22. The outside diameter of oil seal I11 and the outer ring of bearing I18 contact end plate I9I which is bolted to cases 2| and 22 by a series of screws (not shown) passing through flange I82.

- Between adapter I15 and sleeve 21| of master clutch 21 on portion I84 of shaft 24 is mounted a spacer I85. Sleeve 21I contacts shoulder I86 of shaft 24. Portion I81 of shaft 24 provides a running fit for two bushings I88 and I89 secured in housing 26. Washer 289 provides a running fit between shoulder I99 of shaft 24 and housins 26.

On portion |9I is mounted an anti-friction bearing I92 which contacts shoulder I93 of shaft 24. Bearing I92 is mounted in seat I94 at jbint of cases 2| and 22. Sleeve 212 of master clutch 28 contacts inner race of bearing I92 and is secured in position by nut I95 which is at the extreme inner end of driving shaft 24.

The internal construction of master clutches 21 and 28 are identical so a description of clutch 28 will suffice for both. Referring now also to Figs. 14, 16 and 17, the inner surface of cage body I91 is. formed to provide a cylindrical rollway 214. The outer surface of sleeve 212 forms a cooperating rollway having three raised portions 215, each of which has tapered surfaces 216 and 211. Ring 212 is suitably keyed to shaft 24 by key 218.

Disposed in the rollways are three pairs of double rolls 219, 289. These rolls are identical in construction, each comprising enlarged cylindrical ends or drums 28I connected by a reduced mid-portion 282.

For controlling the positions of double rolls 219 and 289 with respect to the tapered portions 216, 211, two similar control rings 283 and 284 are provided. Each control ring has three enlargements or abutments 285 and reduced connecting portions 286. The two connecting portions 286 are fitted side by side within the reduced mid-portions 282 of the double rolls, as indicated particularly in Fig. 14.

For rotatably shifting the control rings 283, 284, sliding keys 2 I9, 229 are provided, these keys being set in shaft 24. Keys 2I9 and 229 have camways 299, 29I (Figs. 18 and 19) in which work pins 292, 293 having rounded heads. Pin 292 is connected to control ring 283 and pin 293 is connected to control ring 284.

For holding the main rolls 219 and 289 against the abutments 285 of the main control rings 283, 284, a series of spring assemblies are provided. Each spring assembly comprises a pair of shoes 294 having spaced rollers journalled thereon contacting the drums 28I of the rolls 219, 289 (like rollers 3I5 in Fig. 24). Shoes 294 have seats in which are disposed helical springs 295. The cooperation between rolls 219, 289 and tapered surfaces'216 and 211 depends upon the relative positions of these parts, which in turn are controlled by the positions of sliding keys 2I9 and 229.

sliding keys 2I9, 229 have additionalcamways 296 and 291 for pins 298, 299 secured to similar control rings for controlling master clutch 21.

The master clutches 21 and 28 are controlled by the sliding keys 2I9, 229, For operating keys 2I9, 229 the following construction is provided. On spacer I (Fig. 13) is slidably mounted a thimble 2I8 secured to sliding keys 2I9 and 229 by pins 22I and 22'2. In groove of thimble 2|8 (Fig. 15) is mounted a shifting shoe 223 supported on two pivot pins 224 and'225, which are secured infork 226 by two screws 221, 228 and lock nuts 229, 238, respectively.

Fork 226 is secured to shaft 23| by key (not shown) and screw and lock nut 232 and 233, respectively. Shaft 23| has two bearings 234 and 235 (Fig. in case 22. shaft 23| is restrained by collar 236 against end of boss 231 and by suitable control connection (not shown) against the outer end of boss 238.

Referring now to Figs. 6, 16, 18 and 19, theoperation of clutches 21 and 28 will be described. The shift fork 226 and keys 2|9 and 228 are shown in their midway or central positions. When the thimble 2 I8 is at its extreme right-hand position (Fig. 6) the keys 2 I9 and 228 are likewise in their extreme right-hand positions and pins 298 and 299 of clutch 21 and pins 292 and 293 of clutch 28 are at positions indicated by A, Figs. 18 and 19. Thepins are now in such position as to hold the double rolls 219 and 288 of both clutches away from their tapered surfaces 216 and 211 and no drive can be transmitted through either,

clutch.

This condition exists only when pivots 84 and H4 and 9| and |2|, respectively, are in line as shown in Fig. 30, .and explained later, and is governed by a control mechanism (not shown); This position-is for the purpose of allowing the engine, as in an automobile, to be started and warmed up without operating any of the working parts of the device but is never used to throw out the mechanism while under power. Means for throwing out under power will be explained later.

When thimble2l8 is moved to the left from position A (Fig. 6), the keys H9 and 228 are likewise moved to the left So that pins 298 and 29s of clutch 21 and pins 292 and 2930f clutch 28 take the positions shown at B. From the shape of the camways, it will be seen that no movement has been imparted to pins 292 and 293 of clutch 28, but pins 298 and 299 of clutch 21 have moved apart, moving control rings 2'83 and 284 to permit the springs 295 of the spring assemblies to move both double rolls 2'19'and 288 against the tapered surfaces 216 and 211, thus tightly locking the case 213 to ring 21| of clutch 21 so that power may be transmitted in either direction of rotation. 3

When this has taken place and the engine is running, the fulcrum'points 84 and 4 can be operated in either direction, either manually or automatically through the control mechanism (not. shown), to provide any ratio, infinitely, be.-

tween the driving and driven shafts.

When the speed of the driven shaft 25 equals the speed of the driving shaft 24, the control mechanism (not shown) moves the thimble 2|8 still further to the left, and keys 2|3 and 228 cause pins 298 and 299 of clutch 21 and pins 292 and 293 of clutch 28 to take the position in- :licated by C. It will be seen that no motion has :aken place to affect clutch 21 but pins 292 and 293 of clutch 28 have moved away from each )ther, moving control rings 283 and 284 to pernit the springs 295 of the spring assemblies to nove both double rolls 219 and 288 against the ;apered surfaces 216 and 211, thus tightly locking ;he case I91 to ring212 of clutch 28 so that power nay be transmitted in either direction of rota- ;ion. It will be noted that at this point both :lutches 21 and 28 are engaged. Now, as the :eys H9 and 228 continue their movement to the eft, the pins 798 and 299 of clutch 2'1 and pins Endwise movement of 28, which is secured by nut I98.

at D. When in this position, it will be seen that pins 292 and 293 of clutch 28 have not changed their positions and that clutch 28 re.- mains in its engaged position, but pins 298 and 299 of clutch 21 have moved together, moving rings 283 and 284 which move the double rolls 219 and 288 away from the tapered surfaces 216 and 211, thus disengaging clutch 21 which throws out the gear, cams, reciprocating slides and working beams from operation'and permitting direct drive from driving shaft 24 to' driven shaft 25.

To return from direct drive to'any lower speed of the driven shaft, the thimble 2|8 and keys 2| 9 and 228 are moved to the right (Figs. 6, 18 and 19) from their extreme left-hand position, and the aforesaid functions are reversed, namely, clutch 21 engages and brings the gear, cams, racks and working beams into action, under no load, while direct drive clutch is still engaged. Then clutch 28 releases, disconnecting shafts 24 and 25. The adjustable fulcrums can then operate for variable ratios. When the pivots 84 and 4 are in line with pivots 9| and |2|, respectively, where no motion or drive is imparted to the driven shaft (Fig. 30) then and only then can the keys 2| 9 and 228"be movedto the extreme right, as described above.

Thus the clutches 21 and 28 have four main positions: A, no drive through either clutch; B, clutch 28 released and clutch 21 locked; C, both clutches locked; and D, clutch 28 locked with clutch 21 released.

For a more detailed disclosure of ,master clutches 21 and 28, attention is called to copending application Serial No. 304,489, filed November 15, 1939.

Referring now'to Figs. 22-25, the parts more or less closely associated with driven shaft 25 will nowbe described. On the inner splined end of driven shaft 25 is the housing I 91 of master clutch On the hub of housing |91 is mounted an anti-friction bearing I 99 whose inner race contacts shoulder 288 of housing 191 and a spacer 28| which fits on shaft 25. Bearing I99 is seated in, the case.

The other end of spacer 28| contacts the inner race of anti-friction bearing 54 which in turn abuts sleeve 38| of overrunning clutch Thence the following members are placed in abutting relation on shaft 25-inner race of bearing 382, spacers 28'3, inner race of antifriction bearing 383, sleeve 384 of overrunning clutch H8, inner race of bearing 385 and sleeve 285 which abuts against collar 284, integral with shaft 25. collar 284 of shaft 25 by nut |98.on end of shaft 25.

On sleeve 285 of shaft 25 is slida-bly mounted clutch thimble 286 (Figs. 6, 21, 22) secured to sliding key 66 by pin 386. In the groove of thimble 286 is mounted shifting shoe 281 (see also Fig. 11) supported ontwo pivot pins 288 and 289 which. are secured in clutch fork 2|8. Fork 2|8 is fixed to shaft 2 which has a hearing at either end, 2|2 and 2|3, in case 22. Endwise movement of shaft 2| is restrained by collar 2 against boss of bearing2|6 and by suitable control connection (not shown) against the outer end of bearing boss 2|8.

A torque limiting device 239 (Figs. 5, 6, 22 and 29) is incorporated in the driven shaft 25. Thedriven shaft 25 is broken for this purpose,-the rear part, indicated by 335 (Fig. 6), being secured to plate 33|, and the forwardpart, indi- 292 and 293 of clutch 28 take the positions shown- All these parts are clamped against cated by 335, being secured to driving plate 332. The driven shaft portion 335 is part of a universal joint 331 to which the load is connected. Shaft 335 is joumalled in the case by a suitable bearing 338. Plate 33| has a series of rollers radially journalled therein and plate 332 has radially extending, axially facing recesses in which the rollers seat. The coil spring 333 operating against collar 334, which is mounted on shaft 335 against collar 204, yieldably holds the rollers and grooves in engagement.

For normal operating torques, the spring 333 is sufi'icient to prevent relative movement between plates 33| and 332. When safe torques are exceeded, the pressure of spring 333 is not suflicient to hold the rollers and grooves in engagement and these plates may slide one upon the other until the excess torque is removed, at which time the rollers automatically re-seat themselves in the grooves.

contained torque limiting device, attention is called to copending application Serial No. 308,109, filed December 8, 1939.

The internal construction of overrunning clutches H and I38 are similar so a description of clutch I I0 will sufiice for both. Referring now also to Figs. 22-25, cage 301 has a gear I09 secured thereto seating the outer race of bearing assembly 303. A cap 308 closes one end of cage 301 and seats the outer race of roller bearing assembly 305.

Fitted around shaft 25 and keyed thereto at 309 is the ring 304 with three specially shaped raised portions 3I0. Fitted between the bore of cage 30] and the ring 304, between the raised portions 3|0', are three double rolls 3I2. Each double roll 3|2 has enlarged roll or drum portions connected by a reduced portion 3 I3. Fitted into bore of cage 301 and free to move therein is a control ring 3 held sideways in the space formed by the reduced portions 3|3 of rolls 3|2. I Bearing on rolls 3I2, on each side, are smaller contact rollers 3I5 .(Fig. 24). These are axially curved or rounded and are carried on spring blocks 3|5 and held against rolls 3I2 by springs 3|1 bearing against spring blocks 3|5 and ring 3. Control ring 3|4 is recessed in three places to receive springs 3I1, spring blocks 3|5 and rolls 3|2.

Also fitted and held in control ring 3I4 is a pin 3|8 having a rounded head which bears in cam groove 3|9 in sliding key 55. By moving sliding key 55 axially of shaft 25 one way or the other from the neutral position shown, the ring 3 is turned one way or the other, making the rolls 3|2 effective on tapers 320 or tapers 32| of the raised portions 3|0 of ring 304 for overrunning operation in one direction or the other.

As illustrated, the device in its neutral position with the control pin 3|8 in the central portion of groove 3I9 of sliding key 55 and with the rolls 3 I 2 held in their free positions between the raised portions 3I0 of control ring 304 by the balanced springs 3I1. In this position the cage 301 is free to revolve relative to the shaft 25 in either direction.

' Sliding key 55 has a second camway 322 in which works pin 323 secured to control ring 324 for similarly controlling clutch I38. This clutch is also shown in its neutral position. The cam grooves 3|9 and 322 are so shaped that shifting of the sliding key 55 rotates the control rings 3 and 324 in the same direction. Shifting of the control rings disturm the balance between the spring assemblies positioning the doublerolls, causing the rolls to engage one set of tapered surfaces 320, or the other set 32I, depending on the direction of shift of the control ring. Thus, when the sliding key 55 is shifted, say, to the left in Fig. 22, clutches H0 and I38 have overrunning characteristics in such directions as to impart continuous rotation to the driven shaft 25 in one direction. Shifting of key' 55 to the right from-- neutral in Fig. 22 reverses the'direction'of continuous rotation of the driven shaft 25. For a more detailed disclosure of clutches H0 and I38, attention is called to copending application Serial No. 304,488, filed November 15, 1939. Referring now to Figs. 5 and 13, the operating parts of the transmission will now be described. 011 drive sleeve 25 of clutch'21 is secured two cams 30 and 3| and an intermittent gear 32 and on housing 213 is a counterbalance 33 for counterbalancing the off-center characteristics of these members and thereby placing the entire driving assembly on shaft 24 in static and dynamic balance (see Fig. 20)

Intermittent gear 32 (Fig. 9) meshes racks 34 and 35 on carrier slides 40 and 4| respectively.

Cam 30 (Figs. 7 and 8) is in contact with follower rolls 35 and 31. Cam 3| (Fig. 9) is in contact with follower rolls 38 and 39. Roll 35 is mounted in lever 42; roll 31 is mounted in lever 43; roll 38 is mounted inlever 44 and roll 39 is mounted inlever 45. I

The driven end of lever 42 is mounted on slide 4| (Figs. 7 and 8) at pivot 45. The fulcrum end of lever 42 is at pivot 41 of lever 48 which is mounted at pivot 43 of case 22. The driven end of lever 43 is mounted on slide 40 at pivot 50. The fulcrum end of lever 43 is at pivot 5| of lever 52 mounted at pivot 53 of case'2I. The driven end of lever 44 is mounted on slide 40 at pivot 54. The fulcrum end of lever 44 is at pivot 55 of lever 55 mounted at pivot 51 of. case 2|. The driven end of lever is mounted in slide 4| at pivot 58.

V The fulcrum end of lever 45 is at pivot 59 of lever 60 mounted at pivot 5|0 of case 22.

Pivots 50 and 54 are secured in slide 40 and on them and in bosses of levers 43 and 44 are mounted anti-friction bearings 24I and 242. Pivots 45 and 58 are secured in slide 4| and on them and in bosses of levers 42 and 45 are mounted anti-fricare secured in levers 42, 43, 44 and 45 and on these pivots and inside rolls 35, 31, 38 and 39 are rzrgzunted anti-friction bearings 253, 254, 255 and Driving slide 40 is guided in a straight line motion by two rods 5| and 52 fixed in the walls of case 22 (Fig. 6). One end of rods 5| and 52 (Fig. 4) is free to move axially in sleeves '53 and F 55 in the case, while other ends are held axially.

in the case between shoulders 51 and 58 and nuts 59 and 10. This is to take care of expansion and contraction. Similarly, driving slide 4| is guided in a straight line motion by two rods 1| and 12 supported in sleeves 13, 14, 15 and 15, respectively, in walls of case 2 I. One end of rods 1| and 12 is free to move axially in sleeves 13 and 15,v while other ends are held axially between shoulders 11 and 18 and nuts 19 and 80.

The inner side of slide 40 has a pivot 8| (Fig. 6) on which is mounted roller bearing 339, at

' alongside gear I85.

which one end of working beam 82 is mounted and is free to oscillate thereon. Beam 82 is mounted in holder 83 (Fig. 10) and is free to slide therein on gib 339. Holder 83 is journalled on pivot 84 by bearing assemblies 251, 258. Pivot 84 is secured in fulcrum slide 85. Slide 85 is adjusted longitudinally by two screws 86 and 81. Screws 86 and 81 are mounted in nuts 88 and 89, respectively, which are secured in slide 85. A1; one end of beam 82 are internal ways 98 in which is mounted pivot slide 9|, of which pivot end is mounted in bearing 92 of driven slide 93.

Driven slide 93 is guided in a, straight line motion by two rods 94 and 95 supported in sleeves 96, 91, 98 and 99, respectively, in walls of case 22 (Figs. 5, 6 and 10). One end of rods 94 and 95 is free to move axially in sleeves 96 and 98, while other ends are held axially between shoulders I88 and |8| and nuts I82 and I83.

Driven slide 93 has a rack I84 (Fig. 10) secured thereto which meshes with a spur gear I85. Gear I85 is mounted on an anti-friction bearing I86 which in turn is mounted on a stud I81 which is secured in support I 88, part of which is integral with one case 2| and part of which is integral with the other case 22. Gear I85 meshes with and drives gear I89 mounted on housing 381 of overrunning clutch 8 (Fig. 22).

The inner side of driving slide 4| has a pivot I II on which is mounted roller bearing 348, at which one end of working beam 2 is mounted and is free to oscillate thereon. Beam I I2 is mounted in holder 3 and is free to slide therein. Holder 3 is journalled on pivot 4 by bearing assemblies 259, 268 and pivot H4 is supported by slide II5. Slide 5 is adjusted longitudinally by two screws 6 and H1. Screws 6 and Ill are mounted in nuts 8 and H9, respectively, secured in slide I I5.

At one end of beam 2 are internal Ways I28 in which is mounted pivot slide |2| whose pivot end is mounted in bearing I 22 of driven slide I23.

Driven slide I23 is guided in a straight line motion by two rods I24 and I25 which are supported in sleeves I26, I21, I28 and I29, respectively, in walls of case 2|. One end of rods I24 and I25 is free to move axially in sleeves I26 and I28, while other. ends are held axially between shoulders I38 and |3| and nuts I32 and I33.

Driven slide I23 has a rack I34 (Fig. se

cured thereto which meshes with a spur gear I35 Gear I35 is mounted in an anti-friction bearing I36, which in turn is mounted on the above-mentioned stud I81 secured in support I88 at joint of cases 2| and 22. Gear I35 meshes with and drives gear. I31 secured to the housing of overrunning clutch I38.

It will be noted that all driving and driven slides 48, 4|, 93 and I23 have afiixed thereto renewable bushings, indicated in general by 269,

slidable on their respective rods.

Fulcrum slide 85 is guided in ways I39 and I48 (Fig. 10) in case 22 and is fitted sidewise by glb |4| and held down by two gibs I42 and I43. Screws 86 and 81 are mounted on anti-friction bearings I44 and I45 (Fig. 4) mounted in supporting bearing housings of case 22 and held down by caps I48 and I49. These bearings take.

(Fig. 6) mounted on sleeve I56, which inturn Screws I I6 and 1 are mounted in anti-friction bearings of case 2| and held down by caps I69 and I18. These bearings take the radial and end thrusts of screws 6 and H1. On splined end of screws 6 and H1 are .mounted gears HI and I12 which are secured in place by nuts I13 and I14. Gears Ill and I12 both mesh with central gear I54.

Central gear I54 is controlled by a pinion 34| on shaft 342 (Figs. 5 and 12). Rotation of shaft 342 by suitable control devices; .(not shown) moves fulcrum slides and H5. uniformly without any binding of the operating screws.

For a clearer understanding of the operation of the control cams 38 and 3|, segment gear 32 and racks 34 and 35, in addition to Figs. 7, 8 and 9, attention is called to Figs. 26, 27 and 28. There are two slides 48 and 4|, two racks 34 and 35, two cams 38 and 3| and four followers 36, 31, 38 and 39. Each cam operates on two followers, one for each rack. This provides positive operation of each slide in each direction. It will be seen from Fig. 8 that clockwise rotation of cam 38 positively moves slides 48 to the right and slide 4| to the left. Likewise, it will be seen from Fig. 9 that clockwise rotation of cam 3| moves slide 4| to the right and slide 48 to the left.

In other words, as illustrated in Fig. 28, oppositely disposed followers 36 and 39 movingwith slide 4| are held at substantially constant distances apart by the relation and shape of the cams 38 and 3|. moving with slide 48 positively control the position of slide 48. Cams 38 and 3| may be exactly alike but positioned at the proper angle.

It will be noted that each follower system comprises a comparatively long swinging lever directly supporting the follower and pivoted to its respective slide, and a comparatively short connecting link connecting the free end of the swinging lever and adjacent fulcrum point on the casing. These levers obviate the necessity for any sliding action in any of the pivots. This peculiar lever construction must, of course, be taken into consideration in the design of the cams and assists in obtaining the desired harmonic motion as hereinafter explained more in detail.

Each slide 48 and 4| partakes of a power' stroke in one direction and a return" or idle stroke in the other direction for a given direction of rotation of the cams, the power strokes being inopposite directions. Cam 38 may be termed the power cam and cam 3| the return cam when the cams .are operating in a clockwise direction in Figs. '7 8, 9 and 28.

During the power stroke, the cam drive is reenforced by the engagement between the seg- Similarly, followers 31 and 38 

